Fluid meter



July 19, 1938.' w. c. WAGNER 2,123,978

FLUID METER 4 Filed Dec. '7, 1935 5 Sheets-Sheet 2 July 19, 193s. w WAGNER 2,123,978

FLUID METER Filed Dec. '7, 1935 5 Sheets-Sheet 5 July 19,1938. w. CT WAGNER 2,123,978

FLUID METER Filed Dec. '7. 1935 5 Sheets-Sheet 4 waff/Ww? W/IWESS.'

Patented July 1e, 193s UNITED STATES .PATENT `oI-#Flce 9 claims.

This invention relates to meteringV the flow of liquids, gases and vapors, and in particular to the metering of the ow of steam.

Heretofore steam or fluid meters have bee rather complicated, and their performance, particularly at light loads as related to rating, has

been relatively unsatisfactory.

One object of my invention is to provide a meter built along relatively simpler lines, and which can be constructed at a lower cost than the present types.

Another object of my invention is to provide in a single meter a more accurate means of measuring down to extremely small loads.

A further object of my invention is to provide a meter which within itself will compensate for variations in the pressure of the supply.

Othervobjects of the invention will appear from the following description at the end of which the invention will be claimed.

Myinvention consists essentially of a pressure tight housing, which incloses a float connected by suitable linkages to an integrating mechanism. An extension of theprinciples makes possible the application of mechanical arrangements whereby in a single meter a plurality of cams can be arranged to operate in different load ranges, and to integrate their respective deflections on the same integrating mechanism.

Generally, but more specifically stated, the inn vention consists in an integrating registering or recording mechanism, a plunger for actuating said mechanism, means for reciprocating the plunger with a constant number of strokes per unit of time, said means including a yieldable connection, a step cam device aligned with the plunger and adapted to limit its stroke in accordance with the position of the cam device since the position of the cam device varies with the load on the meter, one or more float devices each respectively responsive either to the dilferential pressure across an orifice or to the upstream or absolute pressure on the orifice, connections between one of the float devices and the cam device and connections between the' other float device and the plunger and the integrating registering or recording mechanism, the iirst mentioned connection being available for operation due to differential pressure even at low load and both of said connections being `available for operation with pressure compensation, as desired.

The invention also comprises the improvements to be presently described and finally claimed.

The invention broadly and both as to detailsv of construction and combination of parts will be best understood from the following description of specific embodiments, which will be given in connection with the accompanying drawings, in

which:V

Figure 1 is a side elevation, partly in section, of a device embodying features of the invention.

Figure 2 is a detail of a modification of the cam contacting device.

Figurev 3 is a top view of Figure 2.

Figures 4 and 5 are details of additional modifications of the cam contacting device.

Figure 6 is a modification of the cam contacting device to insure greater accuracy at low readings.

Figure 'l is a modification of Figure 6.

Figures 8 and 9 are a side and an edge view of another modification of Figure 6.

Figure 10 is a modification of Figure 1, arranged so that electrical impulses may be transmitted to a pressure compensator in accordance with my co-pending application No. 30,209 led July 6, 1935.

Figure 11 is a. modification of Figure l in which the differential meter herein described is mechanically combined with my pressure compensator into one meter case.

Figure 12 is a-modification of Figure 1, in which the electric motor drive is replaced by a springdriven mechanism.

Figures 13 and 14 are modifications of Figure 12.

Figure 15 is a perspective view of a modified form of casing, and

Figure 16 is a modification of the device shown in Figure 13.

Referring to Figure 1, the meter consists of a pressure-tight housing l into which is screwed. a spark plug 2, which provides a pressure-tight means of making an electrical connection to the constant-speed electric motor 3, said motor providing impulses at uniform intervals for actuating the meter register. Worm 4 mounted on the shaft of motor 3 engages Worm gear 5, imparting uniform rotation to the latter. Pin 6 attached to worm gear 5 presses against loose collar 'l on connecting rod 8, and due to the compression of spring 9, pin 6 is normally constrained toward the extreme end of slot in connecting rod 8. The reciprocating motion of connecting rod 8 is imparted to the plunger rod I0 moving in guides, the extreme or contacting end of plunger l0 being fitted with an adjustable cap H to permit of proper zero setting. The limit of travel of plunger I0 is determined by the edge of cam I2. When contact between plunger le and cam l2 occurs before worm gear d has completed a half revolution, further moi wise direction).

end o the slot, and the cycle is completed when pin e returns to'the starting position, shown in dottedV lines at b-A. The resultant reciprocating motion of plunger l@ is transmitted, by means `of racl` i3, to gear lll turning freely on shaft l5.

To gear i@ isv fastened arm l@ and segment il. The oscillating motion of segment ll is communicated to ratchet wheel ld by means of pawls is, the mtter being soA spaced or staggered as to. permit advancing 'ratchet wheel ld fractional distances of one tooth. A stationary segment 2li and set of pawls, similar in construction to segment il and pawls lb, prevent reverse motion of ratchet wheel i@ on the return stroke oi arm it. mie intermittent unidirectional rotation of ratchet wheel lll is communicated by usual means to register dial pointers 2l which revolve in front of dials 22. 'Motor 3, worm d, worm gear 5, pin d, collar l, spring d, rod 3, plunger lll, rack lii,gear ifi, shaft l5, arm le, pawls l@ and ratchet-wheel lll thus form a variable-stroke, synchronous,

reciprocating, step-by-step compressible motor means.

rection.

The degree oi? motion Yoi plunger l@ is limited by cam i2 whose contact edge is cut into a series of numerous small steps whose edges are, resspectively, parallel and at right angles to the contacting end ll 'of plunger, so that there shall be, during the time of contact between plunger and cern, no resultant force tending to bend or move either the plunger or cam in a vertical di rihe contour of cam isinl the general shape of a parabola whose axis lies on the line 23 and verter at the point 26'.' Vertical motion of the caml is caused by oat iioating on the surface of the mercury 2S, the motion ci' float 25 being transmitted to cam l2 by means of the iioat f stem. il is provided with a vertical strip which is iree to move vertically in dried guide 2l, the latter being placed so as to be horizontally opposite plunger ld, to eliminate possible bending moment on cam l2 due to the rorceof contact. The lower guide is provided by the' float itseli,I there being only a small clearance between neat, and the cylindrical chamber or tube 2li,

` so that any1 error introduced by lateral motion oi heat shall be negligible.

it all loads less than full load, contact between plunger l@ and camV l wld occur before a half revolutlon'of worm wheel E has been completed;

and subsequent motion of pin il in the slot will, by the compression of spring il, press plunger l@ against cam l2 with sumcient iorce to prevent free vertical motion of the latter after said contact has been made. There will be no registration error, since the construction insures acom= plete release of constraint due to said contact, after some instant during the return motion ci pin il, after which'oat 255 and cam l2 are free `to assume a new position properly related to the amants which is mountedin the pipe assembly 3d. The above pressure diierential is then communicated vby tubes or pipes 3l and 32, and thence, respec= tively, into the meter space 3S and the annular chamber ed. The spaces 35 and Se in chambers, above the level of the mercury, are lled ywith water, as is also space til, below the bottom line ofthe oil inthe chamber silit being understood that the housing l is filled with oil. The cham'- 1 ber space 'de will then be subject to the lower pressure, and the chamber space be, which is open at the top, will be subject to the higher pressure. The mercury level in chamber 2d will then fall,

g and the level in chamber i3d will rise, the two v cause themercury in chamber 3d to fall.

By way oi further' explanation it may be said that as shown in 4Flgiue l. there is a partition separatingthe casing into upper and lower parts '-33 and dfi and 2li is anopen ended tube extending through the partition and dipping into the lower part o the chamber i3d.

Toe bottom of mercury chamber 3d is a closeiltting piston 3@ which may be moved up or down 'to adjust themercury level for zero load. The clearance between piston'and the inner wall ci the mercury chamber 8d is a minimum, to pre-u vent leakage of the mercury past the piston. ln addition, a pipe communicates between the general meter space 33 and theclearance space underneath'piston dil, so that the diiderence in pressureon opposite sides of the piston shall be no greater than the actual pressure diderential being measured, plus the pressure head due to the height .ci the mercury column. To provide a pressuretight seal and at the same time permit l of an occasional adjustment of the mercury level,

piston 3b is provided with a threaded extension dll which is screwed through a bottom projection oiq chamber, and provided with a locking nut. The adjustment is covered by means oi cap di, melting a presstu'e-tight seal.

A dierent type of cam structure is shown in Figures 2 and 3, in which the cam 02e, originally laid out in a shape similar to cam it ci Figure l, is bent into a cylindrical shape and fastened to the inner surface of the cylinder the latter being fastened to the stem of the oat 25 (Fig. l) and provided with a vertical strip moving in guide 2l? oi a stationary supporting bracket di), to prevent rotatlon of the cylinder. Gear dd, bevel gear dii and collars le are mounted on hollow spindle il and rotate as one unit, the upper end or bracket d3 acting as one bearing. Alignment of the spindle is insured by the oat stem, which is free `to move vertically thru spindle lll, the latteralso ,acting as a bearing or upper guide for the rioat stem.K Rack de, fastened to the end ci plunger lb, meshes with gear dd' so that linear motion oi plunger lila is converted into angular motion of spindle il which carries at itsl lower end projecting finger di] which swings around and maires contact with cam l. Adjustment of the zero position of plunger lll is by means of the turnbucMe-coupling 5d. The oscillating motion of I to gear 52, which transmits its motion to the register mechanism in the same manner as is done by gear I4 in Figure 1.

A second modification of the cam mechanism is shown in Figure 4. Here the cam I 2b is laid out on polar coordinates, the edges of the steps being radii and circular arcs, but maintaining the original parabolic (or square root) relationship between the horizontal movement permitted the plunger IIBb and the degree of angular motion of the cam, the latter being directly proportional to the vertical motion of float stem. Gear 53 and cam I2b are mounted on shaft 54, gear 53 meshing with rack 55 which is fastened to the float stem. Zero adjustment of the plunger I0b is made by means of screw tip I Ib.

A third modification of the cam structure I2c is shown in Figure 5. The layout of the contact surface of cam I2c is basically the same as for the cam of Figure 4 except that due to the limitations of the structure of Figure 5, cam I2 is designed to be rotated thru a maximum angle not exceeding, say, 90. Cam I2c is fastened to arm 56 which is pivoted on shaft 51, cam and arm being balanced by a. counter-weight. Float stem moves arm 56 by means of pin 58 which engages slot 59. Guide 60 maintains the float stem in a fixed vertical line.

A fourth modification of the cam structure is shown in Figure 6, which permits of greater accuracy at low load readings. Due to the characteristics of the parabolic lcontour of cam I2 in Figure 1, since a minimum vertical distance is required on each of the steps to insure a positive stop for plunger I0, the horizontal distance between successive steps increases at the lower end of the cam, corresponding to low load values, with the result that there are fewer steps on the cam between the zero and 50% load positions of the plunger than between 50% load and full load, and this condition is aggravated as lower loads are reached. The same limitation applies equally to the cylindrical cam of Figure 2 and the radial plate cams of Figures 4 and 5. Assuming the necessity of such steps or notches, accuracy can only be increased by increasing their number. This is accomplished in Figure 6 by employing two simultaneously operating cams I2d and I2 cam I2 1l corresponding to the cam of the preceding figures and being operated over the entire load range from zero to full load, while cam I2e is operative only from zero to, say 20% load. Both cams are preferably of the same size, their mechanical interconnection being such that cam i2e moves from zero thru its entire range while cam I2d moves from zero to a predetermined fractional part of full load range, this being, preferably up to 20% Aor one-fifth of full load. The cam of Figure 4 is shown asbelng so used in Figure 6, although it is understood that any of the cam types shown so far may be combined for this purpose by means of suitable linkage or gearing.

Referring to Figure 6, full load cam I2d and gear 53d are mounted on a common shaft. Rack 55d, carried on the float stem, meshes with gear 53d. Fractional load cam I2e and gear 6I are mounted on a common-shaft. Sectors 62 and 53 are mounted on another common shaft. Rack 55e, carried on the iioat stem, meshes with sector 63 and sector 62 meshes with gear 6I. After the float stem has risen to a point where cam I2d has turned thru 20% of its range, cam I2 has turned thru its complete range, due to the multiplying action of gear 6I and sector 62. Further upward motion of the float stem will continue rotation of the full load cam- I 2d, whereas the smooth portion 66 of rack 55e will slide along the smooth convex surface 65 and the edge of the last tooth of sector 63, without causing any further rotation of sector and consequently without further rotation of cam I2. On the return travel o f the float stem, spiral spring 66 provides for positive reengagement of sector 63 and rack 55". It will be evident from the figure thatcam IZ'-l must make less than one revolution, to prevent contact 4between plunger Ille and cam I2e at higher loads with consequent falsification of the registration.

Also in Figure 6, gear B1 and arm 68 are mounted on a common shaft. Plunger I0d is reciprocated by motor 3 (Fig. l) and plunger I0 is reciprocated by the connection comprised by arm 68. Forward motion of plunger II)d to the right causes arm 68 to swing to the right by means of pin and slot connection 68. The motion of arm r 68 is communicated to plunger I0 by means of slot or notch 10 engaging pin 1 I. Since the angular speed of cam I2e is greater than that of cam I2d, the steps in the contour of cam I2e will recede inward at a faster rate than will those of cam I2d, consequently the forward speed of plunger IEIe must be greater than the forward speed -of plunger Il),d in a ratio which is equal to the angular speed ratios of cams I2e and I2, This ratio is obtained by suitably proportioning the effective lever arm length between the pivot of the arm 68 and pin 1I, and between that pivot and pin at 69. To prevent further motion of plunger I0 beyond the limit set by cam I2e, slot or notch 10 is cut open at the extreme end of arm 68 so that when said limit is reached, the rear or pushing end 12 is of such a length that it will disengage pin 1 I thereby permitting further motion of arm 68 to the full load position. On the return motion of arm 68, the extra length of the forward end 13 of slot will cause positive reengagement of the slot and pin 1I. During the low load position,'in which it is desired to govern the travel of plunger I0d entirely by means of cam I2e, cam I2d is cut away so that plunger tip I Id will contact cam I2d only when cam I2 3 has turned thru its complete range. During this interval, contact between plunger mechanism and cams is entirely thru plunger tip IIe.

A modification of the mechanism connecting the two plunger rods in Figure 6 is shown in Figure '1. Sector 15 and gear 14 are mounted on a common shaft. Rack carried on full load plunger rod Illf meshes with gear 14. Sectors 16 and 11 are mounted on common shaft. Rack, carried on fractional load plunger I0, meshes with sector 11. Motion of plunger IIlt is then communicated to plunger I0! thru gear 14, sectors 15, 16 and 11. When plunger If has completed a predetermined fractional part of its stroke, the smooth convex surface 18 of sector 16 will slide along the edge of the last tooth and the convex surface 19 of sector without causing any further rotation of sector 15 and consequently without causing further motion of plunger |02, which will have reached the limit of its travel. The spiral spring 80 will then cause positive reengagement of sectors 16 and 15 on the return travel of plunger Inf.

A modification of the mechanism connecting the two cams in Figure 6 is shown in Figures 8 and 9. Gears SI and 82 are mounted on a common shaft. Cam I2 and pinion 83 rotate as one unit, being threaded internally and turning on the xed screw 8l. Gear BI meshes with pinion 83, which is suiiiciently long to remain always in mesh therewith, and rack 55h, carried on float stem,l meshes with ge 82. Only the fractional load cam i211 is in Figures 8 and 9 and the connectionto the full load cam at the upper end of the oat stem being the same as in Figure will be able to contact the plunger tip lih for the full axial. width of said steps. As the iloat stem continues to rise, further rotation of cam i211 will cause it, together with pinion t3, to progress axially along screw tl so that at the end of one complete revolution the cam is completely to one side of plunger tip Mh, said process continuing as f pressure compensating meter.

y'long as the float stemcontinues to rise.

On the downward motion of the oat stem as the load drops, cam 21i will again progress along screw di! and will be brought into position opposite plungerl tip i B-remaining in said operating position only throughout the low load' operating range.

The device shown in Figure 6, with its modiications ,shown in lFigures '7, 8 and 9, is `primarily designed to increase the number of teeth or steps in the cam at low loads. It will be evident to those skilled in the art that in actual construction the steps in all of the cams shown in Figures l to il inclusive may be made much smaller and more closely spaced than shown in the figures, their smailness being limited only by the necessity ci making a positive contact with the edge oi the plunger rod tip. 1

Figure l0 shows a'ineans whereby the device may have its function combined with that of my pressure compensating meter. The device shown in Egure l0 is mainly identical with that of Figure l, except that the register gear train is omitted, registration being accomplished on the the magnitude of the periodic reciprocating motion of the plunger rod is limited by the contour of com iii. The motion of rack. is transmitted to sector it, arm it, and segment il', which are rigidly connected as one unit and rotate freely on shaft lb pawls i9 being pivotally mounted on segment ill. tate together and are fastened to shaft iEi, their periodicl angular advance being in a counterclccliwlse direction, as shown in the figure. Mercury switch et is supported in holder free to swing about aids ill. in arm, fastened to the holder, terminates in cam iollower lit. As cam @il rotates, its contour will periodically raise cam follower tid, thereby tilting mercury switch t@ so that the mercury will ow to the left-hand end oi switch-making an electrical connection between electrical contacts Figure l0 shows the device in the closed contact position. Upon closing said contact, an impulse is transmitted to the pressure compensating meter and is registered thereon. .After the high point -ofone ofv the teeth on cam tit has passed camiollower tit, the latter will fall radially inward toward shaft l, thereby tilting mercury switch @t in the opposite direction, and opening the electrical contact. t will be seen that the number of electrical impulses transmitted in a given time interval by mercury switch @t is proportional to the number of revolutions of cam t5 during the said time interval, winch in turn is proportional to the rate of steam ow.

As in Figure i,

Ratchet wheel it and cam 85 roy a-,iaaere Figure 11 shows a modification whereby the decompensator in a single meter housing. The pressure compensator oat mechanism consists of a cylindrical mercury container 9b separated from walls Si of the meter housing. The ligure shows the pressure compensator oat mechanisrn to the left of the differential pressure oat chamber Sit. The pressure compensator mercury container consists of annular chamber s@ whose lower part is iled with mercury and whose upper part 92 contains an entrapped gas, such as air,

which is noncon'densible at ordinary temperatures; a large cylindrical chamber and a smallercylindrical chamber Sil. Float Q5 rides on the mercury column in the latter chamber, which is open at its lower end and communicates with chamber 9d.. The upper end of chamber @il opens directly into chamber @3, which in turn is open at the top. Space 96 and chambers b3, tl, 35 and 36, below the oil in vthe housing, y and above the mercury levels in said chambers, are filled with water. above is iilled with oil. The mercurycontainer @t is arranged to be vertically adjustable while in vice of Figure 1 is combined with my pressure v It will be understood that the meter body y service by means of a threaded projecting stem,

lock-nut and pressure-tight cap, similar in every respect to the vertical adjustment provided for the piston Stof the dierentiall. pressure meter iloat chamberjtlfly l y Float t5 is prevented from rising out of chamber tliupon release of pressure by stops till. The vertical motion of neat stem te, moving in guide "titi, is translatedl into angular motion of cam leverV it@ and pivotal cam liti, by means of slot and pin connection i532. Cam follower itil, contacting the surface ci* cam' lili, is rigidly Vattached to bar tilt which forms a connecting yolre between the-two bearings it. The latter are pivotally connected :to arms it which swing about fixed bearings. The rising and falling of 'cam follower it@ with variations in pressure, due

.thence to a set oi register dials as anuncompensated steam ow reading, the arrangement `being similar to the device shown in Figure l.

The motion of plunger l@ is transmitted to lever it@ by means of pin and slot connection tile. Lever itil is free to swing about fixed bearing, and its motion is transmitted to auxiliary shaft iov it?! by means of slot and pin connection lit. i

The degree oi motion of plunger it and shaft itl will then always be in a definite ratio depending upon the relative length of the effective lever arm to the pin and slot connections tilt and il@ a vertical displacement oi shaft or rod it? either up or' down will vary the above ratio. Rach iii, mounted on shaft or rod itl, engages gear M2 which is on shaft lit, journaled in bearings. Inl order to keep rack lil and gear il@ constantly in mesh at all positions of rack il i, the axial length of gear lit is greater than the width of the faceof rack iii. The oscillating motion oi gear H2 is then transmitted by a ratchet wheel mechanism similar to that shown 7s in Figure 1, to a second setcf register dials as a compensated steam flow reading.

The device of Figure 11 is shown at the zero or return position of plunger I0. In this position lever |08 and. shaft IIS are parallel, so that a shift in position offauxiliary shaft |01, dueto a variation in steam pressure at this time. will not cause motion of gear II2 and consequent registration independently of the motion of plunger I0.

If a compensated reading only is desired, rack I3, sector I4 and all the associated ratchet wheel and register gear mechanism may be omitted.

Counter-weights attached to arms |06. almost wholly compensate for the combined weight of arms, bearings |05, yoke |04, and shaft |01 so that the necessary work done by cam IOI in raising cam follower |03 shall be a minimum.

To facilitate adjustment of the mechanism,

markings I2Amay be attached to the differential pressure cam I2 and markings IOIA to the pressure compensating cam I|0I (Figure 11). Said markings co-operate with fixed guide 21 and cam follower |03, respectively. Said scales are preferably mounted adjacent to the register-dials of the meter and being visible thru the cover glass. The scale pertaining to the differential pressure cam is marked to indicate the proper zero load position of said cam, while the scale pertaining to the pressure compensating cam is directly calibrated to read in pounds pressure.

In the modincation shown in Fig. 11, pipe 3| communicates with the space between piston 38 and the bottom of the chamber.

In operation, the mercury chambers are filled with mercury to a predetermined height or level, and the rest ofthe space within the meter housling is filled with electric insulating oil, which also acts as a lubricant for the various moving parts of the meter mechanism. Before installation, and with both upstream and downstream connecting pipe taps 2| and 32 open to the atmosphere (giving an equalized pressure condition corresponding to zero load) the position of the pointer on the scale is noted, and if there is a deection from the zero indication, the vpiston forming the bottom of the chamber is raised'or lowered until zero load position is correctly indicated. The

- same procedure is followed for adjusting the position of the float and cam of Figure 1, which does not contain the pressure compensating mechanism.

To adjust the pressure compensating mecha- .nism of Figure 11, oil pressure with a test pressure gauge is applied to the upstream pipe tap (the downstream or low pressure pipe-being temporarily capped) and the reading of the pointer attached to the pressure compensating cam is noted; if said pressure reading is not the same as that indicated on the test gauge, the entire mercury chamber of the pressure compensating mechanism is adjusted up or down by means of the threaded. adjusting stem underneath until the pointer indicates the correct pressure. f

After both load and pressure adjustments have been made, the sealing caps underneath the mercury chambers are screwed into place and the device is ready for installation. The steam pressure acting on the space within the meter compresses the gas at 92, forcing the mercury level from chamber 94 dow'n to'chamber 90, within the operating range of float. The condensed water accompanying the steam will eventually displace vall oil below the level H4. Operation of the meter will then commence as soon as motor 0 is connected to a source of electric current.

Although for clarity of illustration my invention has been shown as consisting 0f a. rectangu lar case or shell containing the greater part of the mechanism, with a set of cylindrical casings containing the float chambers, neverthelesss it will be understood by those skilled in the art that the general shape of the meter housing may be considerably altered without departing from the spirit of my invention. For example, the entire mechanism may be enclosed in a cylindrical body as shown in Fig. 15 at IA, as in the l case of my pressure compensators.

diluted or added to by extraneous fluids may be used, the exact density of said liquid being immaterial, since with the comparatively large operating pressure encountered in service, the level of the liquid in the compensator float chamber is determined mainly by the compressibility of the gas in the space S2.

Figure 12 shows a modification of the driving mechanism of Figure 1, which eliminates. the necessity for a source of electric current to actuate the registration mechanism. A spring-wound motor 3 imparts its motion to a drivinggear I il (shown in the figure behind the main body of the spring motor), said gear meshing with pinion IIS. Pinion IIS, gear IIS and bevel gear H1 are mounted on common shaft. Gear I I6 meshes with gear I I8, the latter gear being mounted with arm IIS on common shaft |20. The rotation of gear II8 imparts a reciprocating motion to connecting rod 8 and plunger I0 in a manner similar to the device of Figure 1. The speed o'f the mechanism is controlled by a speed governor (not shown) preferably of the escapement wheel type.

Due to the fact that the speed of a spring-driven mechanism gradually becomes less as unwinding of the spring proceeds, the revolutions of gear III will not always occur at uniformly spaced time intervals. To avoid the more expensive arrangements which are necessary to compensate for diminishing spring power in an accurate time-keeping. device, Figure 12 shows a definite and reliable manner in which such variations may be compensated for. Bevel gear II1 meshes with bevel pinion I2I, the latter being mounted on the shaft of revolution counter |22. The gear ratio between bevel gears I I1 and I2I is preferably the same as the gear ratio between gears IIS andY 'in service what the normal number of such oscillations should be during a given unit of time, and by making note of the actual elapsed time hetween two successive readings of the steam censumption, then by dividing said number of oseillations as recorded on counter |22 by the expected normal number during said time, a ratio or percentage will be obtained which, when dispring motor 3a.

then cause rotation of gear i3d and consequent vided into the Asteam consumption indicated on dials d2@ during the same time, will give the to be wound up. Pawl 25, catches in the teethof ratchet wheel H23 and prevents unwinding. Bevel gear 02d-, meshing with bevel gear id, is mounted on shaft H21 which is journaled at its upper end in a bearing, the lower end of said shaft passing thru a stuing box 28, said stuiiing box permitting rotation oi shaft il with a minimum loss oi uid due to leakage. The lower'end of shaft i'li is squared to permit attaching a portable handle (not shown) whereby the device may be wound up.

In Figure l2, the body ia of the meter is shown as being suciently deep so that the lower part contains water, the water level being at the same height as the water level of Figure 1, in orderv -that any leakage thru the stulng box will be water, which is automatically replaced by further condensation in the pipes connecting to the steam line, rather than the insulating oil with which the upper part of the meter body is filled. Such leakage wili, however, occur only at such times as the device is wound up; the lower part of the meter housing having an extension with an externally threaded portion to which the packing gland of the stuiing box is screwed, and another externally threaded portion of larger diameter to which is screwed a cover or cap H29, with ring gasket '936, placed between making a pressure tight seal.

Efigure i3 is almodihcation of Figure 12, in which the spring motor is continuously wound up by an auxiliary electric motor. Worm iti, mounted onf the shaft oi electric motor ist?, meshes with worm gear B38. Gear H33 and worm i3d are mountedon shaft 35 which is journaled in bearings. Worm 68d meshes with worm gear i3d, the latter beingfastened to the shaft of The rotation of motor 32 will winding up of the spring motor. It will be evi- 'i dent to those smiled inthe art that the driving torque of electric motor 32 can be so adjusted that no damage will result to the gear train between said motor and spring motor Se when the latter is completely wound up, and that, moreover, the normal speed of gear H35 can be designed so as to be only slightly in excess of the normal unwinding speed of the spring contained within spring motor 3, so as to maintain the speed of electric motor G32 near its normal value. The reduction gearing 4shown in the figure should preferably contain one or more worm gear drives.

since such a drive is in general irreversible, if the worm is made with a proper pitch, so that in case of interruption to the electric current supply. there will be no `tendency -for the spring to unwind by driving the electric motor backwards.

f With the construction shown in the ligure, therefore, .the ratchet and pawl of Figure 12 may be. omitted. 'I'he co'nnecting mechanismV between the spring motor and pusher 'rod is understood to be the same as in Figure12. vThe modica'tion. 1 have shown in` Figure 13 is one of greatest accuracy and reliability, since with the spring motor cap and shoulder,

graders maintained at or near the maximumwound up l spring motor may be accomplished in several ways, one of which is shown in Fig. 16.' This is an arrangement whereby the tension of the spring within the spring motor actuates a switch or contact in such a manner that the electric motor will wind up the spring whenever the tension of said spring falls below a predetermined value. this modification consists of a casing i containing a spring motor 38 of which the spring exerts a torque in a counter-clockwise direction on the gear E35. Worm 113i, vonnected to the shaft of the rotor of motor 532, meshes with worm-wheel 633 on shaft 35. Worm i3d meshes with gear i3@ and is keyed on shaft H35 by means As shown in greater detail in Fig. i6,

of key 262. Spring du@ stresses worm i3d toward 'collar 2H by the reaction of spring 2t@ against collar 263. Contact 2% is mounted on spring 29d for engagement or contact with 2cd' which is` vmounted on a yoke pivoted at 282, the upper end 2cd. The operation of this modication is as follows:

Y en the spring of motor 38 becomes too weak to resist the clockwise thrust of spring "itil, spring 2t@ pushes worm i3d over against collar 2H and thus closes contacts 263 and 2135. Current is conducted through'lead 28d, motor 632, lead N9, contacts 263 and Ebb, electro-magnet 29%, and back to the source through lead 2id. Motor E32 is thus actuated by spring motor 3B to wind up the spring. The increasing tension of the spring of motor 3 becomes strong enough to overcome the tension of spring 2b@ and worm i3d is slid to theright, which tends to break contacts 293 and 2cd. However, due to the attraction of electro-magnet 2t@ for armature 2d?, springsupport 23d is bent to the right until its tension. becomes suicient to overcome the slight attraction of magnet '2th, at which time spring 2M! breaks contacts 2li@ and it-with a snap, which prevents arcing. y

Figure 14 is a modification of Figure 13 in which the spring motor is continuously wound up by a water wheel which is actuated by the water condensed within the body of the meter. A discharge nozzle isi, having a relatively ne bore, is screwed into the bottom i meter casing is.

Water from nozzle impinges against the buckets 'of water wheel or turbine E3B, Worm its and the rotatable shaft toextend thru the meterv housing with a. minimuml amount of leakage of water past the'bearing surface within saidproiectionV Bevel gear MI meshes with bevel gear M3, the latter being mounted on the shaft ot springmotor 3B so thatjrotation of bevel gear M3 will wind up the spring motor. The lower bearing of the vertical shaft is a part of water wheel chamber or housing |44 which is fastened to the meter housing. Opening |45 in the bottom of chamber |44 permits the escape of water discharged from the water wheel buckets, said water falling into tank |46 which is fastened to meter housing. Tank |46 is open to the atmosphere thru openings |41, to provide for escape of steam in case of accidental leakage from the bottom of the meter. Pipe |48 communicates between tank |46 and a nearby drain for disposing of the water discharged from the Water wheel.

In Figure 14, the meter body is filled with insulating oil above the level of the water, while water occupies the space `below this line. To provide a supply of water for steam meters, present practise in the art is to install reservoirs or chambers in the pipes transmitting pressure from the steam line to the meter, said reservoirs being of comparatively large area and provided fin-ther with a set of radiating fins mounted on said tubes to dissipate the heat of the steam and provide for condensation. It will be evident to vthose skilledin the art that said reservoirs and fins may be made of any size necessary in order lto assure a constant supply of water to replace the water withdrawn from the meter casing by the operation of the water wheel or turbine.

Any of the methods of furnishing the motive power above illustrated in Figures 1, 12, 13 and 14 may obviously be combined with any of the cam types shown in Figures 1, 3, 5, 6, 'l and 9 to produce a steam meter operating on the vprinciple herein described. It will likewise be evident that the plunger stroke counter |22 of Figure 12 may be adapted to any of the l various types of my device in order to increase the accuracy and reliability of the meter. Y

It will be obvious to those skilled in the art that the invention is not limited in respect to details of construction and arrangement or to matters of mere form or otherwise than the prior art may require.

I claimz- 1. A fluid meter comprising in combination, an integrating register, a motor, reciprocating compressible means including a pawl-and-ratchet driven by said motor and driving the register and also including a stroke adjustment, a step camdevice for limiting the stroke of said means by compression thereof, and two float mechanisms whereof one is connected with and adapted to position said cam device in response to differential pressureat an orice and whereof the other is connected with said stroke adjustment and is responsive to inlet side pressure at the orifice.

2. A fluid meter comprising in combination, a pressure tight housing containing oil, a chamber depending from the housing and containing a supply of mercury, a partition separating Athe chamber into upperand lower parts, a tube extending through the partition and dipping into the lower part of the chamber, a supply of water above the partition and under the oil and on top of the mercury and in the tube, a supply of water below the partition and on top of the mercury, diiferential pressure taps to the respective supplies of water, a float in the tube and on the mercury; an integrating register, a motor, variable stroke mechanism operated by said motoi and actuating the register step-by-step, and a step cam device actuated by the float and operative to limit the stroke of said mechanism.

3. A pressure tight housing containing a supply of oil, two mercury chambers depending from -cury in one of the chambers, an integrating register, a motor, variable stroke reciprocating means driven by said motor and driving the register, step-bystep, a oat arranged in the other chamber and responsive to differential pressure and provided with a step cam cooperating with said reciprocating means to limit its stroke, and a second float in the one chamber responsive to inlet pressure and provided with connections for adjusting the stroke of said means whereby the register does respond to variation of inlet pressure at an oriiice.

4. A fluid meter comprising, in combination, an integrating register, a motor arranged to actuate said register, adjustable means forming a connection between said motor and said register whereby said motor actuates said register, a cam controlling said adjustable means, first means controlling said cam, an orifice device controlling said rst means in response tb differential pressure at said orifice, second means controlling said adjustable means separately from said cam, and 4means controlling the position of said second means in response to inlet pressure at said orifice.

5. A fluid meter comprising,l in combination, an integrating register, a motor arranged to actuate said register, adjustable means forming a connection between said -rnotor and said register whereby said motor actuates said register, a cam controlling said adjustable means, first means controlling said cam, anoriflce device controlling said first means in response to differential pressure at said orifice, second means controlling said adjustable means separately from said cam. means controlling the position of said second means in response to inlet pressure at said orifice, and an adjustable connection between said second means and said adjustable means, said adjustable connection being operatively located between said cam and said register.

6. A fluid meter comprising, in combination, an integrating register, a motor arranged to actuate said register, adjustable means forming a connection between said motor and said register whereby said motor actuates said register, a cam controlling said adjustable means, iirst means controlling said cam, an orifice device controlling said first means in response to diil'erential pressure at said orifice, second means controlling said adjustable means separately from said cam, means controlling the position of said second means in response to inlet pressure at said orice, and a second register arranged so as to be actuated by said motor under the control of said cam but independent of the control of said second means.

7. A fluid meter comprising in combination, a pressure tight housing containing oil, a chamber depending from the housing and containing a supply of mercury, a partition separating the chamber into upper and lower parts, a tube extending through the partition and dipping into the lower part of the chamber, a supply of water above the partition and under the oil and on top of the mercury and in the tube, a supply oi water below the partition and on top of the mercury, differential pressure taps to the respective supplies of water, a iioat in the tube and on the mercury, an integrating register, a motor, variable-stroke mechanism operated by'said motor and actuating the register step-by-step, a step cam device actuated by the iioat and operative to limit the stroke of said mechanism, an adjustable piston head forming the lower wall of the lower part of said chamber, and a connection from beneath said piston head to the exterior of the housing and serving for adjustment of said piston head.

t. A uid meter comprising, in combination, an

integrating register, a motor arranged to actuate said register, adjustable means forming a cona nection between said motor and said register whereby said motor actuates said register, a cam controlling said adjustable means, vfirst means controlling said cam, a device controlling said irst means in response to dierentlal pressure at said device, second means controlling said .adjustable means separately from said cam,r and of the housing.

assente means controlling the position of said second means in response to inlet pressure at said device. l

chamber into upper and lower parts, a tube extending through the partition and dipping into the lower part of the chamber, a supply of Water above the partition and under the` oil and on top of the mercury and in the tube, a supply of water below the partition and on top of the mercury, differential. pressure taps to the respective supplies of water, a oat in the tubeand on the mercury, an integrating register, a motor, variable-stroke mechanism operated by said motor and actuating the register step-by-step, a step cam device actuated by the oat and operative to limit the stroke or" saidmechanism, an adjustable piston head forming the lower waii of the lower part of said chamber, and a conduit from beneath said piston head to the interior Waarna awnerina l 

